|Publication number||US6259166 B1|
|Application number||US 09/429,006|
|Publication date||Jul 10, 2001|
|Filing date||Oct 29, 1999|
|Priority date||Oct 30, 1998|
|Also published as||DE19850052A1|
|Publication number||09429006, 429006, US 6259166 B1, US 6259166B1, US-B1-6259166, US6259166 B1, US6259166B1|
|Original Assignee||Asea Brown Boveri Ag|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (10), Non-Patent Citations (2), Referenced by (9), Classifications (9), Legal Events (4)|
|External Links: USPTO, USPTO Assignment, Espacenet|
The present invention relates to a generator with double driving machinery. This application claims priority under 35 U.S.C. §§119 and/or 365 to 198 50 052.1 filed in Germany on Oct. 30, 1998; the entire content of which is hereby incorporated by reference.
Generators with double driving machinery are known, for example, from “Allianz Report,” February, 1998, page 72, and are used in power plant installations. The generator is typically arranged in what is called a single-shaft system between a gas turbine and a steam turbine, as shown in FIG. 1.2 of the cited document. The generator also includes a slip ring unit electrically connected with it, which is located on the same shaft as the generator. In such single-shaft systems, static excitation devices are installed starting with an excitation current of greater than 2000 amps, whereby the static excitation devices supply the generator rotor winding via the slip ring unit with an excitation current of up to 7000 amps. Up to an excitation current of about 2000 amps, either static excitation devices or brushless excitation machines may be used on the generator shaft.
At least on one side or on both sides of the generator shaft, the generator is connected via a transmission gear with the gas turbine and the steam turbine. Such a transmission gear in this case functions, for example, as a frequency converter to adapt 60 Hz turbines (speed: 3600 rpm) to 50 Hz generators (speed: 3000 rpm), or as a converter that converts from a supersynchronous to a synchronous speed. In addition, an SSS coupling can be used between the steam turbine and the generator, whereupon a coupling of both machines will only be possible after they reach their operating speed.
It was found that in such conventional single-shaft systems with transmission gears, the performance is limited with respect to the mechanical and electrical design. The slip ring device or the slip ring shaft cannot be constructed with a desired diameter size, since the peripheral speed of the brush face at the slip rings is limited to approximately 80 m/s. Up to 80 m/s, a good contact with the brushes for transmitting the excitation current can be ensured. For a 60 Hz generator with 2-pole design, this limit of 80 m/s is reached with a slip ring diameter of 400 mm. A slip ring diameter of 400 mm permits a slip ring shaft diameter of approximately 290 mm. But the shaft diameter of 290 mm limits the maximum mechanical power transfer to approximately 100 MW turbine power if the shaft is manufactured from a steel suitable for generator rotors. This power transmission limit takes into account both the permanent moments to be transmitted by the shaft, and interference forces, such as missynchronizations and short-circuit cutoff.
Single-shaft systems of the known type require a special mechanical design of the shaft bearing which directly adjoins the slip ring unit. The entire torque of the steam turbine is transmitted via this shaft bearing to the generator, whereby the slip ring unit represents only a comparatively small weight load, and the shaft bearing therefore requires a correspondingly complex design.
In addition, a conventional slip ring shaft has, on one side, a coupling flange that has been worked in one piece from this shaft, and, on the other side, a welded-on or shrunk-on coupling that is attached to the slip ring shaft after the slip rings have been installed. The slip rings cannot be installed on a slip ring shaft over a coupling flange.
It is an object of the present invention to further develop a generator with double driving machinery of the initially mentioned type, in such a way that greater mechanical power can be transmitted from the driving machines to the generator shaft than is possible with previously known generators.
In particular, an object is to create a generator with double driving machinery in which greater mechanical power can be transmitted on the generator shaft on the side of the slip ring unit, and whereby the slip ring shaft and its bearing can be designed in a simpler manner.
According to the invention, the objects of the invention can be realized by providing a generator with double driving machinery that has between the generator shaft and the slip ring shaft a first gear shaft of a transmission gear, and that a driving machine on the side of the slip ring unit is, via a second gear shaft of the transmission gear, connected with the generator shaft.
It is especially advantageous if the torque transmitted by the driving machine on the side of the slip ring unit is delivered to the generator shaft without mechanical stress on the slip ring shaft. The dimensions of the slip ring shaft and of the slip rings themselves are, therefore, only subject to the electrical conditions for the various peripheral speeds. Furthermore, the slip ring shaft only has a coupling flange on one side, which makes slip rings easier to uninstall and reinstall.
It is particularly advantageous if the transmission gear is designed only for the mechanical torque transmission—and is in no way related to the electrical design of a slip ring unit.
With the transmission gear provided according to the present invention, between the generator and the slip ring unit, it is possible to markedly increase the mechanical power transmitted by a driving machine on the side of the slip ring unit, compared to the state of the art, without mechanically stressing the slip ring shaft.
Still other objects, features, and attendant advantages of the present invention will become apparent to those skilled in the art from a reading of the following detailed description of embodiments, taken in conjunction with the accompanying drawings.
The following explains the invention in reference to the drawings. Only those elements essential for understanding the invention are shown in the drawing. For example, for reasons of clarity none of the shaft bearings are shown.
FIG. 1 shows a schematic view of a generator with double driving machinery according to a first preferred embodiment of the present invention; and
FIG. 2 shows a schematic view of a generator with double driving machinery according to a second preferred embodiment of the present invention.
FIG. 1 shows a generator 1 with double driving machinery according to a first preferred embodiment of the present invention. A generator shaft 13 b is connected on both sides of the generator 1 with a driving machine, i.e., with a gas turbine 2 and a steam turbine 3. The gas turbine 2 is connected directly via a gas turbine shaft 13 a and a coupling 8 to the generator shaft 13 b. The steam turbine 3 is connected via a steam turbine shaft 13 e, a coupling 12, an intermediate shaft 13 f, a coupling 11, a first and second gear shaft 13 c, 13 g, and a coupling 9, with the generator shaft 13 b. On a side opposite from the generator 1, the first gear shaft 13 c is connected via a coupling 10 with a slip ring unit 4 in order to supply an excitation current to the generator 1.
The generator 1 and the slip ring unit 4, provided for transmitting the generator excitation current, are therefore separated from each other by means of the first gear shaft 13 c. The torque generated by the steam turbine 3 is transferred via the transmission gear 5 to the generator shaft 13 b between the slip ring unit 4 and the generator 1. Therefore, the slip ring unit 4 and associated slip ring shaft 13 d are not subject to any torque stresses generated during operation. As a result, the design of the slip ring shaft 13 d with respect to the slip rings provided on it (not shown) depends substantially on electrical requirements. The parameters for the electrical design of the slip ring unit 4 include essentially, the peripheral speed of the slip rings, which should not exceed 80 m/s, and the current density of the live brushes on the slip rings. Since the slip ring shaft 13 d does not transmit any torque generated by the driving machine, it can have a simple bearing.
In addition to having torque stress eliminated from the slip ring shaft 13 d, the slip ring shaft 13 d is also advantageously equipped only on one side with a flange for the coupling 10. This means that the slip rings shrunk on the slip ring shaft 13 d can be easily pulled off on the side of the slip ring shaft 13 d opposite from the flange, if they become worn during operation.
The generator shaft 13 b and the slip ring shaft 13 d are in part constructed as a hollow shaft, and the first gear shaft 13 c is completely constructed as a hollow shaft. An excitation conductor 7 (indicated by a broken line) is installed in the bores of the generator shaft 13 b, the slip ring shaft 13 d and the gear shaft 13 c. The design of such an excitation conductor 7 in the form of a conductor rail is generally known and, thus, does not need to be explained in more detail. The excitation conductor 7 provides the electrical connection between the slip ring unit 4 and the generator 1 for an excitation current generated with static excitation.
FIG. 2 shows principally the same installation configuration of the generator 1 with double driving machinery as described above in relation to the first preferred embodiment of the present invention. However, the difference is found in the coupling of the steam turbine 3 with the transmission gear 5. The steam turbine 3 is connected via a so-called synchronous coupling 6 or SSS coupling with the transmission gear 5. Such synchronous couplings 6 only permit an activation of the coupling between the first gear shaft 13 g and the steam turbine shaft 13 e when the same speed has been reached by each of the shafts. As would be appreciated by one of ordinary skill in the art, during the start-up phase of the generator 1, the steam turbine 3 is initially uncoupled.
While the invention has been described in detail with reference to preferred embodiments thereof, it will be apparent to one skilled in the art that various changes can be made, and equivalents employed, without departing from the scope of the invention. It would, for example, be feasible to couple the gas turbine 2 via another transmission gear with the generator 1. In this way, the gas turbine 2 also could be operated supersynchronously, and the other transmission gear then would function as a converter. It would also be conceivable to operate the steam turbine 3 supersynchronously, and to then design the transmission gear 5 correspondingly as a speed converter.
2 Gas turbine
3 Steam turbine
4 Slip ring unit
5 Transmission gear
6 Synchronous coupling
7 Excitation conductor
13 a Gas turbine shaft
13 b Generator shaft
13 c, g Gear shaft
13 d Slip ring shaft
13 e Steam turbine shaft
13 f Intermediate shaft
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|U.S. Classification||290/4.00R, 290/52, 310/232|
|International Classification||F01D15/10, H02K7/18|
|Cooperative Classification||F01D15/10, H02K7/1823|
|European Classification||F01D15/10, H02K7/18A2|
|Jul 25, 2000||AS||Assignment|
Owner name: ASEA BROWN BOVERI AG, SWITZERLAND
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TOMMER, JOSEF;REEL/FRAME:011014/0102
Effective date: 19991228
|Nov 26, 2001||AS||Assignment|
Owner name: ALSTOM, FRANCE
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:ASEA BROWN BOVERI AG;REEL/FRAME:012287/0714
Effective date: 20011109
|Jul 11, 2005||LAPS||Lapse for failure to pay maintenance fees|
|Sep 6, 2005||FP||Expired due to failure to pay maintenance fee|
Effective date: 20050710